CN103017403A - Refrigeration device - Google Patents
Refrigeration device Download PDFInfo
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- CN103017403A CN103017403A CN2011102913699A CN201110291369A CN103017403A CN 103017403 A CN103017403 A CN 103017403A CN 2011102913699 A CN2011102913699 A CN 2011102913699A CN 201110291369 A CN201110291369 A CN 201110291369A CN 103017403 A CN103017403 A CN 103017403A
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- 238000005057 refrigeration Methods 0.000 title abstract 2
- 238000001816 cooling Methods 0.000 claims abstract description 98
- 238000010438 heat treatment Methods 0.000 claims abstract description 90
- 239000003507 refrigerant Substances 0.000 claims description 274
- 230000009183 running Effects 0.000 claims description 98
- 238000001704 evaporation Methods 0.000 claims description 20
- 230000008020 evaporation Effects 0.000 claims description 19
- 238000001514 detection method Methods 0.000 claims description 6
- 239000002826 coolant Substances 0.000 abstract description 53
- 239000007788 liquid Substances 0.000 abstract description 29
- 238000000034 method Methods 0.000 description 15
- 230000008569 process Effects 0.000 description 15
- 230000008859 change Effects 0.000 description 12
- 238000009833 condensation Methods 0.000 description 12
- 230000005494 condensation Effects 0.000 description 12
- 239000012071 phase Substances 0.000 description 9
- 238000000926 separation method Methods 0.000 description 9
- 230000015572 biosynthetic process Effects 0.000 description 8
- 102100022406 60S ribosomal protein L10a Human genes 0.000 description 7
- 101000755323 Homo sapiens 60S ribosomal protein L10a Proteins 0.000 description 7
- 238000010586 diagram Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 5
- 230000008676 import Effects 0.000 description 3
- 238000010257 thawing Methods 0.000 description 3
- 238000004804 winding Methods 0.000 description 3
- 230000002159 abnormal effect Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 2
- 239000003638 chemical reducing agent Substances 0.000 description 2
- 239000000498 cooling water Substances 0.000 description 2
- 230000006837 decompression Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- -1 L10B Proteins 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000007791 liquid phase Substances 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
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Abstract
The invention provides a refrigeration device, which is provided with a cooling loop, a heating loop and a cooling and heating loop, wherein the cooling loop enables a coolant to sequentially flow through at least one of a compressor 1, a condenser 2, a liquid receiver 3 and expansion valves 4A and 4B and at least one of evaporators 5A and 5B to cool at least one of a front chamber A and a rear chamber B; the heating loop enables the coolant discharged from the compressor 1 to bypass the condenser 2 and the expansion valves 4A and 4B and flow towards at least one of the evaporators 5A and 5B to heat at least one of the front chamber A and the rear chamber B; and the cooling and heating loop enables the coolant discharged from the compressor 1 to bypass the condenser 2 and flow into the evaporator 5B (or 5A) to be liquefied to heat the rear chamber B (or the front chamber A), and enables the liquefied coolant to flow towards the expansion valve 4A (or 4B) and the other evaporator 5A (or 5B) to be evaporated to cool the front chamber A (or the rear chamber B).
Description
Technical field
The invention relates to and a kind ofly can cool off simultaneously refrigerating plant with the running of heating according to heat pump mode.
Background technology
For example, in van cooler, for two compartments that separation counter inside forms, wherein a side keeps low temperature and the opposing party is kept high temperature, the different commodity of storage temperature of providing and delivering simultaneously whereby.
In addition, for the wherein side with two compartments keeps low temperature and the opposing party is kept high temperature, before be to adopt a kind of " cooling and heating system " (cold and hot system) to be installed on the van cooler, described cooling and heating system are to utilize the warm water heater of cooling water heat of radiator and previous refrigerating plant to combine.
Yet, the warm water heater that is used for above-mentioned cooling and heating system, except arranging the space of needs special use,, shares driver's cab heating installation the cooling water of radiator for being provided, so not enough etc. the problem of the heating installation ability (ability of heating) in the driver's cab of having.
Therefore, in patent documentation 1, propose a kind of system,, cool off and heat according to refrigerant as substantially with the refrigerating plant of previous pattern.This system, to adopt following mode, that is: follow the evaporation of the refrigerant in the common freeze cycle, from around capture evaporation latent heat (be gas phase needed heat by liquid phase transition), cool off whereby a wherein side compartment, and the HTHP gaseous coolant (hot gas) that will spue from compressor, get around condenser and expansion valve and (make the hot gas bypass, namely without condenser and expansion valve), import in the indoor evaporimeter, according to the heat release of the refrigerant in this evaporimeter, the opposing party's that heats compartment (hot gas mode).This situation, if refrigerant is with state (state that adiabatic condensation temperature is high) heat release in evaporimeter of high pressure, then this refrigerant liquefies owing to condensing, because can occuring, liquid refrigerants is inhaled into unfavorable condition in the compressor, so before importing refrigerant in the evaporimeter, according to the decompression means this refrigerant is decompressed to below the indoor temperature saturation pressure, adiabatic condensation temperature is reduced, prevent that refrigerant from condensing.
[previous patent documentation]
(patent documentation)
Patent documentation 1: TOHKEMY 2004-162998 communique
Summary of the invention
[problem that invention institute wish solves]
Yet, the system that in patent documentation, proposes, owing to be to adopt a kind of mode, described mode is in cooling wherein during a side compartment, makes refrigerant condense in condenser (liquefaction), and when heating the opposing party's compartment, make refrigerant get around condenser and expansion valve and flow, therefore, can't side by side cool off and heat, since need to alternatively cool off running and heat running, therefore can the such problem of efficient difference.
Again, when heating, do not utilize the phase change of refrigerant, so can't effectively utilize the latent heat of condensation to be used as thermal source, therefore have the low such problem of heating efficiency yet.
And then, adopting a kind of mode, described mode is when heating, and when the low pressure in refrigerant loop becomes setting value when following, (receiver) is supplemented to refrigerant the refrigerant loop from accumulator.But if the winding number of compressor changes significantly, then FEEDBACK CONTROL postpones, and also has refrigerant and promptly is not supplemented to the such problem of possibility in the refrigerant loop.
The present invention develops in view of the above problems, and its purpose is to provide a kind of refrigerating plant, can cool off simultaneously running and heat running, and can effectively utilize because the phase change of refrigerant is required or the latent heat of generation, improves cooling and heats ability.
[technological means of dealing with problems]
In order to reach above-mentioned purpose, invention claimed in claim 1 is a kind of refrigerating plant, install respectively evaporimeter in two compartments, and described refrigerating plant comprises:
Cooling circuit, described cooling circuit, make that refrigerant sequentially flows through compressor, condenser at least, one of them side in one of them side in two expansion valves installing corresponding to each compartment and above-mentioned two evaporimeters that are connected in parallel, cool off one of them side in two compartments;
Add temperature loops, the described temperature loops that adds makes the refrigerant that spues from above-mentioned compressor, gets around above-mentioned condenser and above-mentioned expansion valve and flows to one of them side in two evaporimeters, one of them side in two compartments of heating whereby; And
Cooling and add temperature loops, described cooling and add temperature loops, make the refrigerant that spues from above-mentioned compressor, get around above-mentioned condenser and an above-mentioned wherein side expansion valve, flow in a side's wherein the evaporimeter and liquefy, then a wherein side the compartment of heating whereby makes refrigerant after the liquefaction flow to the opposing party's expansion valve and the opposing party's evaporimeter and makes its evaporation, cools off whereby the opposing party's compartment.
Invention claimed in claim 2 is for invention claimed in claim 1, wherein:
Between the above-mentioned condenser and above-mentioned expansion valve of above-mentioned cooling circuit, the installing accumulator, and be equiped with refrigerant return pipe road and the additional pipeline of refrigerant; Described refrigerant return pipe road makes by the refrigerant behind the above-mentioned evaporimeter to be back in the above-mentioned accumulator; Described refrigerant replenishes pipeline, from accumulator refrigerant is supplemented to the low-pressure side loop of above-mentioned compressor.
Invention claimed in claim 3 is for claim 1 or 2 described inventions, wherein: on bypass line, the installing flow is adjusted means; Described bypass line makes the refrigerant that spues from above-mentioned compressor, gets around above-mentioned condenser and above-mentioned expansion valve, and flows in each evaporimeter.
Invention claimed in claim 4 is for each the described invention in the claim 1～3, wherein: at most open and close valves of refrigerant pipeline installing, and described refrigerating plant is equiped with control device, in order to control the switching of each open and close valve; Described refrigerant pipeline is in order to consist of above-mentioned cooling circuit, above-mentionedly to add temperature loops, and above-mentioned cooling and add temperature loops.
Invention claimed in claim 5, for invention claimed in claim 4, wherein: installing temperature detection means in above-mentioned each compartment, above-mentioned control device, design temperature for each compartment, according to the mensuration temperature of each compartment of measuring according to the said temperature detection means, come above-mentioned open and close valve is carried out open and close controlling, come whereby selectively to cool off running, the running of heating, and the cooling and the running of heating;
Described cooling running is that refrigerant is flowed in above-mentioned cooling circuit, cools off one of them side in two compartments;
The described running of heating is to make refrigerant flow one of them side in two compartments of heating in above-mentioned adding in the temperature loops;
Described cooling and the running of heating are to make refrigerant in above-mentioned cooling and add in the temperature loops to flow, and cool off a wherein side compartment, and the opposing party's that heats compartment.
Invention claimed in claim 6, for invention claimed in claim 5, wherein: replenish pipeline at above-mentioned refrigerant and install open and close valve, and in the pressure detecting means of refrigerant pipeline installing in order to the suction pressure that detects above-mentioned compressor and the pressure that spues, above-mentioned control device, when coming two compartments are heated according to the above-mentioned running of heating, with specified period, or become setting value when following when the suction pressure according to the detected compressor that comes of above-mentioned pressure detecting means, open above-mentioned open and close valve, refrigerant is supplemented to the low-pressure side loop of compressor from above-mentioned accumulator.
Invention claimed in claim 7, for invention claimed in claim 6, wherein: the installing open and close valve, described open and close valve with so that the refrigerant that spues from above-mentioned compressor toward the flow disruption of above-mentioned condenser direction or unimpeded, when above-mentioned open and close valve is positioned at the running or become more than the setting value according to the pressure that spues of the detected compressor that comes of above-mentioned pressure detecting means in cooling and when running of heating of heating of closed condition, then open above-mentioned open and close valve, if and the pressure that spues of compressor becomes the tolerance bound definite value when above, stop the running of compressor.
Invention claimed in claim 8, for each the described invention in the claim 5～7, wherein: the refrigerant that flows through above-mentioned condenser and above-mentioned evaporimeter, no matter be any situation of above-mentioned cooling running, the above-mentioned running of heating, above-mentioned cooling and the running of heating, all flow toward equidirectional.
[effect]
Invention according to claim 1, the cooling of compartment is to carry out according to common refrigerating plant refrigerant being evaporated in evaporimeter; Heating of compartment is to make the high pressure-temperature gaseous coolant (hot gas) that spues from compressor, gets around condenser and expansion valve and imports in the evaporimeter, according to making the refrigerant heat release carry out (hot gas mode) in this evaporimeter.
On the other hand, when the cooling situation of a side compartment and the opposing party's that heats compartment wherein, make the refrigerant that spues from compressor, get around condenser and a side expansion valve wherein, and flow in a side's wherein the evaporimeter, according to the liquefaction of a described refrigerant wherein side the compartment of heating, then make liquefaction after refrigerant flow to the opposing party's expansion valve and the opposing party's evaporimeter, refrigerant evaporation according to making after the liquefaction can cool off the opposing party's compartment.This kind mode is so-called heat pump mode, and in a side the compartment, the evaporimeter performance is as the function of condenser therein, gaseous coolant is condensed and make phase change, follow this phase change effect, can effectively utilize the large latent heat of condensation of heat and be used as thermal source, thereby can improve the efficient of heating of compartment.And the refrigerant after the liquefaction after being depressurized according to expansion valve, is imported in the opposing party's the evaporimeter of compartment and evaporates, thus can from around capture evaporation latent heat and energy efficiency is cooled off the opposing party's compartment well.Like this, in the present invention, owing to be to adopt heat pump mode, described heat pump mode is to utilize heat between two compartments to move and follow the latent heat that the phase change of refrigerant is required or produce, cool off and heat, therefore, can effectively utilize heat energy to improve cooling and the ability of heating, and can shorten the start-up time of device.
And, in cooling and when running of heating, do not use condenser, make refrigerant circulation owing to get around condenser, thus can side by side cool off running and heat running, and energy efficiency is cooled off goodly and is heated.
Invention according to claim 2, when cooling off and heating running, refrigerant condenses in the evaporimeter of a side compartment therein and liquefies, and the refrigerant after will liquefying stores in accumulator, then, the liquid refrigerants that sends from accumulator, after the expansion valve according to the opposing party is depressurized, in the evaporimeter of inflow the opposing party's compartment, and make its evaporation, and can be used for cooling off the opposing party's compartment, and the running of cooling off unchangeably and heat.Again, for example, the situation make the refrigerant circulation quantity not sufficient in the refrigerant loop owing to the running of heating is supplemented to refrigerant the low-pressure side loop of compressor from accumulator, can supply refrigerant circulation whereby.
Invention according to claim 3, when heating running, make the refrigerant that spues from compressor, get around condenser and expansion valve, before flowing to evaporimeter, limit the flow of this refrigerant and with refrigerant decompression, owing to make this kind formation according to flow adjustment means, the adiabatic condensation temperature of this refrigerant descends, and condenses in evaporimeter and can suppress to a certain extent refrigerant.
Reach according to claim 45 described inventions, design temperature for each compartment, mensuration temperature according to each compartment of measuring according to the temperature detection means, control device is carried out open and close controlling to magnetic valve, can selectively carry out whereby " cooling running ", " running of heating " reaches " cooling off and the running of heating ".
Invention according to claim 6, when according to the running of heating is next two compartments being heated, become setting value when following with specified period or when the suction pressure according to the detected compressor that comes of pressure detecting means, refrigerant is supplemented to the low-pressure side loop of compressor from accumulator, owing to make this kind formation, even the winding number of refrigerator changes significantly, also can prevent the such unfavorable condition of refrigerant circulation quantity not sufficient in refrigerant loop.
Invention according to claim 7, be equiped with open and close valve, described open and close valve with so that the refrigerant that spues from compressor toward the flow disruption of condenser direction or unimpeded, when this open and close valve is positioned at the running or become more than the setting value at the pressure that spues of cooling and when running compressor of heating of heating of closed condition, then open open and close valve, make the refrigerant drainage of a part, if and the pressure that spues of compressor becomes the tolerance bound definite value when above, stop the running of compressor, owing to make this kind formation, the abnormal pressure that can prevent the refrigerant loop rises, and guarantees high security.
Invention according to claim 8, make the refrigerant of the inside of condenser and evaporimeter, no matter be the cooling running, the running of heating, any situation of cooling and the running of heating, when passing through the inside of these parts, refrigerant flows toward equidirectional always, owing to make this kind formation, when change temperature adjustment pattern, do not need compressor is stopped, and, can freely change wherein the temperature adjustment pattern of one compartment, can not be subject to the impact of temperature adjustment pattern of another compartment, for the operation of dispensing of van cooler etc., described van cooler can repeatedly be advanced at short notice or stop and engine is stopped continually, can obtain a kind of effect that the revolution of engine can be effectively utilized in the running of refrigerating plant.
Description of drawings
Fig. 1 is the refrigerant loop diagram (when cooling-cooling is turned round) of refrigerating plant of the present invention;
Fig. 2 is the refrigerant loop diagram (when heating-heating running) of refrigerating plant of the present invention;
Fig. 3 is the refrigerant loop diagram (when cooling off-heating running) of refrigerating plant of the present invention;
Fig. 4 is the flow chart of all flow processs of the control of expression refrigerating plant of the present invention;
Fig. 5 is the flow chart of flow process of the cup temperature adjustment mode decision of expression refrigerating plant of the present invention;
Fig. 6 is the flow chart of flow process of the rear chamber temperature adjustment mode decision of expression refrigerating plant of the present invention;
Fig. 7 is the flow chart of the pressure control flow of expression refrigerating plant of the present invention;
Fig. 8 is the flow chart that the refrigerant of heating of expression refrigerating plant of the present invention is filled the flow process of control;
Fig. 9 is the flow chart of flow process of the solenoid control of expression refrigerating plant of the present invention;
The figure of the on-off action of the magnetic valve when Figure 10 is respectively turning round of expression refrigerating plant of the present invention.
[primary clustering symbol description]
1 compressor
2 condensers
3 accumulators
4A, 4B expansion valve
5A, 5B evaporimeter
6 hydraulic accumulators
7 pressure sensors (pressure detecting means)
8 non-return valves
9,10 temperature sensors (temperature detection means)
11A, 11B non-return valve
12 pressure-regulating valves
13 pressure sensors (pressure detecting means)
14A, 14B flow regulator (flow adjustment means)
15A, 15B non-return valve
16 flow regulators (pressure reducer)
17 controllers (control device)
18 configuration parts
L1～L3, L4A, L4B, L5A, L5B, L6, L7 refrigerant pipeline
L8, L9A, L9B bypass line
L10A, L10B, L11 refrigerant return pipe road
The L12 refrigerant replenishes pipeline
V1, V2A, V2B, V3A, V3B, V4A, V4B, V5 magnetic valve (open and close valve)
The specific embodiment
Below, with reference to drawing example of the present invention is described.
Fig. 1～Fig. 3 is the refrigerant loop diagram of refrigerating plant of the present invention, below, the basic comprising of refrigerating plant is described based on Fig. 1.
The refrigerating plant of this example is will be installed on the van cooler, and the machine as main comprises: compressor 1, condenser 2, accumulator 3, two expansion valve 4A and 4B, two evaporimeter 5A and 5B, and hydraulic accumulator 6.
Above-mentioned compressor 1, driven by revolution according to the engine of icon not, the refrigerant pipeline L1 that extends out from its exhaust end, being connected to the entrance side of above-mentioned condenser 2, is that magnetic valve V1 is installed on this refrigerant pipeline L1 in order to pressure sensor 7 and the open and close valve of the pressure that spues that detects compressor 1.And the refrigerant pipeline L2 from the outlet side of condenser 2 extends out is connected to above-mentioned accumulator 3, and 2 non-return valves 8 that flow are installed on this refrigerant pipeline L2 from accumulator 3 toward condenser in order to stop refrigerant.
In addition, in the not shown counter of van cooler, form by front and back the cup A and the rear chamber B that are separated, above-mentioned evaporimeter 5A, 5B and temperature sensor 9,10 are arranged on respectively in these cups A and the rear chamber B, two evaporimeter 5A, 5B connect in parallel.
Then, from the refrigerant pipeline L3 that above-mentioned accumulator 3 extends out, be branched into two refrigerant pipeline L4A, L4B from the way, each bar refrigerant pipeline L4A, L4B are connected to each entrance side that is separately positioned on evaporimeter 5A, 5B in cup A and the rear chamber B.And open and close valve is magnetic valve V4A, V4B and above-mentioned expansion valve 4A, 4B, installs separately respectively one on these refrigerant pipelines L4A, L4B.
Again, refrigerant pipeline L5A, L5B from the outlet side of each evaporimeter 5A, 5B extends out collaborate into a refrigerant pipeline L6, and refrigerant pipeline L6 is connected to the entrance side of above-mentioned hydraulic accumulator 6.And open and close valve is magnetic valve V3A, V3B and non-return valve 11A, 11B in order to stop refrigerant to flow from hydraulic accumulator 6 toward evaporimeter 5A, 5B, installs separately respectively one on refrigerant pipeline L5A, L5B, and pressure-regulating valve 12 is installed on the refrigerant pipeline L6.Again, from the refrigerant pipeline L7 that the outlet side of hydraulic accumulator 6 extends out, be connected to the suction side of compressor, the pressure sensor 13 in order to the suction pressure that detects compressor 1 is installed on this refrigerant pipeline L7.
On the other hand, bypass line L8, from bifurcated between the pressure sensor 7 of above-mentioned refrigerant pipeline L1 and the magnetic valve V1 out, described bypass line L8 is with so that refrigerant gets around above-mentioned condenser 2, above-mentioned accumulator 3 and above-mentioned expansion valve 4A, 4B; This bypass line L8 is branched into two bypass line L9A, L9B from the way, these bypass lines L9A, L9B are connected between each expansion valve 4A, 4B and each evaporimeter 5A, 5B of above-mentioned refrigerant pipeline L4A, L4B.And open and close valve is flow regulator 14A, the 14B of magnetic valve V2A, V2B and capillary or choke valve etc., installs separately respectively one on each bypass line L9A, L9B.
Again, refrigerant return pipe road L10A, L10B, respectively from bifurcated between each evaporimeter 5A, 5B of above-mentioned refrigerant pipeline L5A, L5B and each magnetic valve V3A, the V3B out, these refrigerant return pipe roads L10A, L10B, interflow and become a refrigerant return pipe road L11.And, refrigerant return pipe road L11, be connected between the above-mentioned non-return valve 8 and above-mentioned accumulator 3 of above-mentioned refrigerant pipeline L2, in order to allow that refrigerant from non-return valve 15A, 15B that the past accumulator 3 of each evaporimeter 5A, 5B flows, is installed in respectively on refrigerant return pipe road L10A, the L10B.
And then the additional pipeline L12 of refrigerant begins to extend from the bottom of accumulator 3, and this refrigerant replenishes pipeline L12, is connected between the above-mentioned pressure-regulating valve 12 and above-mentioned hydraulic accumulator 6 of refrigerant pipeline L6.And open and close valve is magnetic valve V5 and flow regulator 16, is installed in refrigerant and replenishes on the pipeline L12.
In addition, the refrigerating plant of this example, being provided with control device is controller 17, said temperature sensor 9, temperature sensor 10, pressure sensor 7, pressure sensor 13, and magnetic valve V1, V2A, V2B, V3A, V3B, V4A, V4B, V5 are electrically connected respectively so far on the controller 17.Again, the configuration part 18 in order to various operating conditions of input temp setting value, pressure set points etc. etc. is connected on the controller 17.
Then, in the refrigerating plant of this example, can select " cooling circuit ", " adding temperature loops " or " cool off and add temperature loops " to carry out " cooling running ", " running of heating ", reach in " cool off and add heat run " any; Described " cooling circuit ", shown in the thick line of Fig. 1, make refrigerant sequentially flow through one of them side among one of them side among compressor 1, condenser 2, accumulator 3, two expansion valve 4A and the 4B, two evaporimeter 5A that are connected in parallel and the 5B, and hydraulic accumulator 6, cool off one of them side with rear chamber B in of cup A (in Fig. 1, representing to cool off the cooling circuit of the situation of cup A and rear chamber B); Described " adding temperature loops ", shown in the thick line of Fig. 2, make the gaseous coolant (hot gas) that spues from compressor 1, get around condenser 2 and flow to one of them side among one of them side among two flow regulator 14A and the 14B, two evaporimeter 5A and the 5B with expansion valve 4A, 4B, reach hydraulic accumulator 6, one of them side in rear chamber B of cup A that heats whereby (situation of in Fig. 2, represent to heat cup A and rear chamber B add temperature loops); Described " cool off and add temperature loops ", shown in the thick line of Fig. 3, make the gaseous coolant (hot gas) that spues from compressor 1, get around condenser 2 and a side expansion valve 4A (or 4B) wherein, flow among a side's wherein the evaporimeter 5B (or 5A) and liquefy, rear chamber B (or cup A) whereby heats, then the expansion valve 4B (or 4A) that makes refrigerant after the liquefaction flow to the opposing party makes its evaporation with the opposing party's evaporimeter 5A (or 5B), cool off whereby cup A (or rear chamber B) (in Fig. 3 expression cooling cup A and heat after chamber B situation cooling and add temperature loops).
Based on Fig. 4～shown in Figure 9 flow chart the control flow according to controller 17 carried out be described, herein.
At first, controller 17, to each design temperature of cup A and rear chamber B with according to temperature sensor 9, the 10 detected cup A that come and rear chamber B respectively measure temperature, compare to judge each temperature adjustment pattern of cup A and rear chamber B.
Namely, if the running of beginning refrigerating plant, then as shown in Figure 4, controller 17, read each design temperature TsF, TsR (step S1) of cup A and rear chamber B, and read according to temperature sensor 9,10 and the cup A that detects respectively and rear chamber B respectively measure temperature T mF, TmR (step S2).Then, judge whether mensuration temperature T mF in cup A is positioned at the scope (step S3) that consideration (has added) the design temperature amplitude (TsF-Td)～(TsF+Td) behind the temperature span of control limit of control Td.Then, mensuration temperature T mF in cup A is not arranged in the situation (judged result at step S3 is the situation of " no (NO) ") of the scope of design temperature amplitude (TsF-Td)～(TsF+Td), then carries out processing shown in Figure 5 (cup temperature adjustment mode decision).
In cup temperature adjustment mode decision shown in Figure 5, judge whether cup A stops (stopping to cool off or heating) (step S11), in the situation (result in step S11 is the situation of "No") that cup A does not stop, judging whether the mensuration temperature T mF in cup A surpasses the higher limit (TsF+Td) (step S12) of design temperature.Mensuration temperature T mF in cup A surpasses the situation (judged result in step S12 is the situation of " being (YES) ") of the higher limit (TsF+Td) of design temperature, cup A is judged as " refrigerating mode " (step S13), and situation about not surpassing, (judged result in step S12 is the situation of "No"), because the mensuration temperature T mF in cup A is lower than the lower limit (TsF-Td) of design temperature, so cup A is judged as warm up mode (step S14), then, processing is transferred to main program shown in Figure 4 (step S15).In the situation (judged result in step S11 is the situation of "Yes") that cup A stops, processing directly being transferred to main program shown in Figure 4 (step S15) again.
Through above processing, judge the temperature adjustment pattern in cup A, about rear chamber B, also carry out the judgement of same temperature adjustment pattern.
That is, as shown in Figure 4, judge whether mensuration temperature T mR in rear chamber B is positioned at the scope (step S4) that consideration (has added) the design temperature amplitude (TsR-Td)～(TsR+Td) behind the temperature span of control limit of control Td.Then, mensuration temperature T mR in rear chamber B is not arranged in the situation (judged result at step S4 is the situation of "No") of the scope of design temperature amplitude (TsR-Td)～(TsR+Td), then carries out processing shown in Figure 6 (rear chamber temperature adjustment mode decision).
In rear chamber temperature adjustment mode decision shown in Figure 6, whether chamber B stops (stopping to cool off or heating) (step S21) after judging, in the situation (result in step S21 is the situation of "No") that rear chamber B does not stop, judging whether the mensuration temperature T mR in rear chamber B surpasses the higher limit (TsR+Td) (step S22) of design temperature.Mensuration temperature T mR in rear chamber B surpasses the situation (judged result in step S22 is the situation of "Yes") of the higher limit (TsR+Td) of design temperature, rear chamber B is judged as " refrigerating mode " (step S23), and situation about not surpassing, (judged result in step S22 is the situation of "No"), because the mensuration temperature T mR in rear chamber B is lower than the lower limit (TsR-Td) of design temperature, chamber B is judged as warm up mode (step S24) after the institute, then, processing is transferred to main program shown in Figure 4 (step S25).In the situation (judged result in step S21 is the situation of "Yes") that rear chamber B stops, processing directly being transferred to main program shown in Figure 4 (step S25) again.
Then, controller 17, to according to the measured value Pml of the suction pressure of pressure sensor 7, the 13 detected compressors 1 that come and measured value Pmh and the setting value Psl of suction pressure and the setting value Psh of the pressure that spues of the pressure that spues, compare, control the refrigerant pressure in the refrigerant loop.
Namely, judging whether to spue, little (Pmh＜Psh) and the measured value Pml of suction pressure are than large (Pml＞Psl) (the step S5 of Fig. 4) of setting value Psl than setting value Psh for the measured value Pmh of pressure, be the situation of "No" in its judged result, carry out pressure control shown in Figure 7.
About pressure control shown in Figure 7, whether the measured value Pmh that judges the pressure that spues is above (Psh≤Pmh) (the step S31) of setting value Psh, be the situation of "Yes" in judged result, magnetic valve V1 opens (opening), the part of gaseous coolant flows toward condenser 2, so the pressure drop that spues (step S32) of compressor 1.Then, whether the measured value Pmh that judges the pressure that spues is tolerance bound definite value above (step S33), be the situation of "Yes" in judged result, compressor (copm) 1 stops (step S34), processes to be transferred to main program shown in Figure 4 (step S35).Again, the judged result in step S33 is the situation of "No", processes directly to be transferred to main program shown in Figure 4 (step S35).
On the other hand, judged result in step S31 is the situation (the measured value Pmh of the pressure that spues is the situation less than setting value Psh) of "No", because the measured value Pml of suction pressure must be below the setting value Psl, opens magnetic valve V5 (step S36) so judge cold medium shortage in the refrigerant loop.So, stored the refrigerant in accumulator 3, replenish the refrigerant pipeline L6 of upstream that pipeline L12 is added to hydraulic accumulator 6 from refrigerant, afterwards, process being transferred to main program shown in Figure 4 (step S35).
Then, as shown in Figure 4, judging whether cooling operational unit (whether one of them side among cup A and the rear chamber B is judged as refrigerating mode) (step S6), is the situation of "No" in its judged result, and the refrigerant of heating shown in Figure 8 is filled control and is carried out.
Fill in the control at the refrigerant of heating shown in Figure 8, all be not cooled at cup A and rear chamber B, and the situation that one of them side among cup A and the rear chamber B is heated (one of them side among cup A and the rear chamber B is judged as the situation of warm up mode), magnetic valve V5 is only with some cycles open hour (Tm2-Tm1), so stored the refrigerant in accumulator 3, replenish pipeline L12 from refrigerant and be added (filling) the refrigerant loop.Also have, from the liquid refrigerants that accumulator 3 is supplied to via the additional pipeline L12 of refrigerant, in the process that flows through the additional pipeline L12 of refrigerant, owing to can be depressurized according to flow regulator 16, its part can be evaporated and gasify.
Namely, at first, operational unit (whether one of them side among cup A and the rear chamber B is judged as warm up mode) (step S41) judges whether to heat, if this judged result is "Yes", then judge whether through stipulated time Tm1 (step S42), in case through stipulated time Tm1 (judged result in step S42 is the situation of "Yes"), judge whether magnetic valve V5 closes (step S43), in the situation (judged result in step S43 is the situation of "Yes") that magnetic valve V5 closes, open magnetic valve V5 (step S44).Also have, the judged result in step S41 is the situation (situation of the operational unit of not heating) of "No", processes to be transferred to main program shown in Figure 4 (step S48).
As above-mentioned, if magnetic valve V5 is opened (step S44), then judge whether to have passed through stipulated time Tm2 (step S45), in case through stipulated time Tm2 (judged result in step S45 is the situation of "Yes"), magnetic valve V5 is closed (step S46), and afterwards, time T m1 is reset (Tm1=0, Tm2=0) (step S47) with Tm2, then, processing is transferred to main program shown in Figure 4 (step S48).
In case the above-mentioned refrigerant filling control of heating is carried out or cooling operational unit (judged result among the step S6 at Fig. 4 is the situation of "Yes") is being arranged, as shown in Figure 4, judge whether running stops (step S7), in the situation (judged result in step S7 is the situation of "Yes") that running stops, compressor (comp) 1 and not shown fan and whole magnetic valve V2A, V2B beyond the magnetic valve V1, V3A, V3B, V4A, V4B are by " OFF (closing) " (step S8).Also have, magnetic valve V1 is normally open valve, if cut off the energising toward magnetic valve, just this magnetic valve can be opened.
On the other hand, situation about not shutting down (judged result in step S7 is the situation of "No"), carry out solenoid control shown in Figure 9.
Namely, if according to handling process shown in Figure 5, come cup A is carried out the temperature adjustment mode decision, and according to handling process shown in Figure 6, rear chamber B is carried out temperature adjustment mode decision (step S51), then according to the temperature adjustment pattern after being judged, magnetic valve V1, V2A, V2B, V3A, V3B, V4A, V4B, as shown in figure 10, for various runnings, be carried out respectively opening and closing operations (step S52), and compressor (comp) 1 and not shown respectively driven control (step S53) of fan, then, processing is transferred to main program shown in Figure 4 (step S54).
Herein, about 1) cooling running, 2) running, 3 of heating) cool off and the running, 4 of heating) running stops, and 5) defrost and turn round, one side is with reference to the on-off action of Fig. 1～refrigerant loop diagram shown in Figure 3 and magnetic valve shown in Figure 10, Yi Bian carry out the following description.
1) cooling running
1-1) cool off together the cooling of cup A and rear chamber B-cooling running:
When cool off together cup A with after the situation of chamber B, as shown in figure 10, shut electromagnetic valve V2A, V2B, other magnetic valve V1, V3A, V3B, V4A, V4B all open.So refrigerant circulates with the cooling circuit shown in the thick line of Fig. 1.
Namely, according to compressor 1 and the compressed high pressure-temperature gaseous coolant that forms, by refrigerant pipeline L1, be imported in the condenser 2, described refrigerant is cooled in condenser 2 and condenses, then according to the liquid refrigerants that condenses after liquefying, by refrigerant pipeline L2, be sent to accumulator 3, then flow by refrigerant pipeline L3 and refrigerant pipeline L4A, L4B from accumulator 3, in this flow process, be depressurized according to expansion valve 4A, 4B.And, liquid refrigerants after being depressurized according to expansion valve 4A, 4B, be imported among evaporimeter 5A, the 5B that is installed in respectively in cup A and the rear chamber B, owing to the liquid refrigerants after described being depressurized in each evaporimeter 5A, 5B from around capture evaporation latent heat and evaporate, so cup A is cooled with rear chamber B.And, be used for cooling off according to evaporation the refrigerant of cup A and rear chamber B, flow from refrigerant pipeline L5A, L5B toward refrigerant pipeline L6 and arrive hydraulic accumulator 6, in this hydraulic accumulator 6 by gas-liquid separation, then, only gaseous coolant flows through refrigerant pipeline L7 and is attracted in the compressor 1, so gaseous coolant is compressed once again according to compressor 1, after, repeatedly carry out same freeze cycle, cool off together cup A and rear chamber B.
1-2) only cool off the then cooling that stops of chamber B of cup A-shut down:
Only cooling off then chamber B situation about being stopped of cup A, as shown in figure 10, state from above-mentioned cooling-cooling running, shut electromagnetic valve V4B, high-pressure liquid refrigerant in condenser 2 after the liquefaction, in flowing through the process of a side refrigerant pipeline L4A wherein, 4A is depressurized according to expansion valve, and only is supplied among the evaporimeter 5A of cup A.Therefore, therein among a side the evaporimeter 5A, refrigerant evaporation and only cup A be cooled.And, for the refrigerant of cooling cup A, flow and arrival hydraulic accumulator 6 from refrigerant pipeline L5A toward refrigerant pipeline L6, by gas-liquid separation, then, only gaseous coolant flows through refrigerant pipeline L7 and is attracted in the compressor 1 in this hydraulic accumulator 6, so gaseous coolant is compressed once again according to compressor 1.And, repeatedly carry out later on same freeze cycle, only cool off cup A.
1-3) chamber B and cup A stops stopping-cooling off running after the cooling only:
The situation that cup A is stopped only cooling off rear chamber B, as shown in figure 10, state from above-mentioned cooling-cooling running, shut electromagnetic valve V4A, high-pressure liquid refrigerant in condenser 2 after the liquefaction, in flowing through the process of a side refrigerant pipeline L4B wherein, 4B is depressurized according to expansion valve, and only is supplied among the evaporimeter 5B of rear chamber B.Therefore, therein among a side the evaporimeter 5B, refrigerant evaporation and only chamber B be cooled.And, for the refrigerant of chamber B after the cooling, flow and arrival hydraulic accumulator 6 from refrigerant pipeline L5B toward refrigerant pipeline L6, by gas-liquid separation, then, only gaseous coolant flows through refrigerant pipeline L7 and is attracted in the compressor 1 in this hydraulic accumulator 6, so gaseous coolant is compressed once again according to compressor 1.And, repeatedly carry out later on same freeze cycle, only chamber B after the cooling.
2) running of heating
2-1) heat the together running of heating-heat of cup A and rear chamber B:
When heat together cup A with after the situation of chamber B, as shown in figure 10, shut electromagnetic valve V1, V4A and V4B, other magnetic valve V2A, V2B, V3A, V3B open.So refrigerant circulates with the temperature loops that adds shown in the thick line of Fig. 2, and according to hot gas mode heat together cup A and rear chamber B.
Namely, according to compressor 1 and the compressed high pressure-temperature gaseous coolant (hot gas) that forms gets around condenser 2, accumulator 3 and expansion valve 4A, 4B, from refrigerant pipeline L1, by bypass line L8, bypass line L9A and L9B, and refrigerant pipeline L4A and L4B, and be imported into each evaporimeter 5A, 5B of cup A and rear chamber B, and, gaseous coolant, when by bypass line L9A, L9B, according to flow regulator 14A, 14B, be limited flow and be depressurized, its adiabatic condensation temperature descends a little.
And, be imported into the gaseous coolant among each evaporimeter 5A, 5B of cup A and rear chamber B, mainly be that the part of described gaseous coolant liquefies owing to condensing according to heat release heat respectively cup A and rear chamber B.So, according to condensing in evaporimeter 5A, 5B, the refrigerant after the part liquefaction, its part is passed through refrigerant pipeline L5A and L5B, refrigerant return pipe road L10A and L10B, is reached refrigerant return pipe road L11, and be imported into accumulator 3, so liquid refrigerants can be stored in accumulator 3.Again, other refrigerant from refrigerant pipeline L5A, L5B, arrives hydraulic accumulator 6 by refrigerant pipeline L6, and by gas-liquid separation, then, only gaseous coolant flows through refrigerant pipeline L7 and is attracted in the compressor 1 in this hydraulic accumulator 6.And gaseous coolant is compressed once again according to compressor 1, repeatedly carries out later on same freeze cycle, and cup A and rear chamber B together heat.
2-2) only heat cup A then chamber B stop heating-shut down:
In the then chamber B situation about being stopped of cup A of only heating, as shown in figure 10, state from the above-mentioned heating-running of heating, shut electromagnetic valve V2B, so, according to compressor 1 and the compressed high pressure-temperature gaseous coolant (hot gas) that forms, from refrigerant pipeline L1, by bypass line L8, bypass line L9A, and refrigerant pipeline L4A, and be imported into the evaporimeter 5A of cup A, and, gaseous coolant is when by bypass line L9A, according to flow regulator 14A, be limited flow and be depressurized, its adiabatic condensation temperature descends a little.
And, be imported into the gaseous coolant among the evaporimeter 5A of cup A, according to heat release and the cup A that only heats, the part of described gaseous coolant is condensed and is liquefied.So, according to the heat release in evaporimeter 5A, the refrigerant after the part liquefaction, its part is passed through refrigerant pipeline L5A, refrigerant return pipe road L10A, is reached refrigerant return pipe road L11, and is imported into accumulator 3, so liquid refrigerants can be stored in accumulator 3.Again, other refrigerant from refrigerant pipeline L5A, arrives hydraulic accumulator 6 by refrigerant pipeline L6, and by gas-liquid separation, then, only gaseous coolant flows through refrigerant pipeline L7 and is attracted in the compressor 1 in this hydraulic accumulator 6.Then, gaseous coolant is compressed once again according to compressor 1, repeatedly carries out later on same freeze cycle, and cup A only heats.
2-3) stop cup A and the rear chamber B that only heats stop-heating running:
Be stopped and the situation of chamber B after only heating at cup A, as shown in figure 10, state from the above-mentioned heating-running of heating, shut electromagnetic valve V2A, so, according to compressor 1 and the compressed high pressure-temperature gaseous coolant that forms, from refrigerant pipeline L1, by bypass line L8, bypass line L9B, and refrigerant pipeline L4B, and be imported into the evaporimeter 5B of rear chamber B, and, gaseous coolant is when by bypass line L9B, according to flow regulator 14B, be limited flow and be depressurized, its adiabatic condensation temperature descends a little.
And, be imported into the gaseous coolant among the evaporimeter 5B of rear chamber B, according to heat release and the rear chamber B that only heats, the part of described gaseous coolant is condensed and is liquefied.So, according to the heat release in evaporimeter 5B, the refrigerant after the part liquefaction, its part is passed through refrigerant pipeline L5B, refrigerant return pipe road L10B, is reached refrigerant return pipe road L11, and is imported into accumulator 3, so liquid refrigerants can be stored in accumulator 3.Again, other refrigerant from refrigerant pipeline L5B, arrives hydraulic accumulator 6 by refrigerant pipeline L6, and by gas-liquid separation, then, only gaseous coolant flows through refrigerant pipeline L7 and is attracted in the compressor 1 in this hydraulic accumulator 6.Then, gaseous coolant is compressed once again according to compressor 1, repeatedly carries out later on same freeze cycle, and rear chamber B only heats.
3) cool off and the running of heating
3-1) the cooling of cooling cup A and the rear chamber B that the heats-running of heating:
The situation of chamber B as cooling cup A and after heating, as shown in figure 10, shut electromagnetic valve V1, V2A, V3B, V4B, other magnetic valve V2B, V3A, V4A open.So refrigerant is with the cooling shown in the thick line of Fig. 3 and add temperature loops (series loop) and circulate, and according to heat pump mode heat rear chamber B and cooling cup A.
Namely, according to compressor 1 and the compressed high pressure-temperature gaseous coolant (hot gas) that forms, get around condenser 2, accumulator 3 and expansion valve 4B, from refrigerant pipeline L1, by bypass line L8, bypass line L9A and refrigerant pipeline L4B, and be imported into the evaporimeter 5B of rear chamber B, and gaseous coolant is when by bypass line L9B, 14B is depressurized according to pressure reducer, and its adiabatic condensation temperature descends a little.
And, be imported into the gaseous coolant among the evaporimeter 5B of rear chamber B, in the evaporimeter 5B of performance as the function of condenser, according to condensing and heat release, the rear chamber B that heats, the major part of described gaseous coolant liquefies owing to condensing.
As above-mentioned, the refrigerant after liquefying according to condensing in evaporimeter 5B by refrigerant pipeline L5B, refrigerant return pipe road L10B, and refrigerant return pipe road L11, and is imported into accumulator 3, so liquid refrigerants can be stored in accumulator 3.And from accumulator 3, the liquid refrigerants of high pressure can be imported into the evaporimeter 5A of cup A by refrigerant pipeline L4A from refrigerant pipeline L3, and liquid refrigerants is when the refrigerant pipeline L4A, is inflated valve 4A throttling and is depressurized.
As above-mentioned, the liquid refrigerants (part can become gaseous state) after being depressurized according to expansion valve 4A, in evaporimeter 5A, from around capture evaporation latent heat, so cup A can be cooled.And, for the refrigerant that cools off cup A according to evaporation, flow and arrival hydraulic accumulator 6 from refrigerant pipeline L5A toward refrigerant pipeline L6, by gas-liquid separation, then, only gaseous coolant flows through refrigerant pipeline L7 and is attracted in the compressor 1 in this hydraulic accumulator 6.Then, gaseous coolant is compressed once again according to compressor 1, repeatedly carries out later on same heat pump cycle, so cup A is cooled and rear chamber B is heated.
The running of heating-cool off of 3-2) heating cup A and cooling off rear chamber B:
The situation of chamber B after heat cup A and cooling, as shown in figure 10,
Shut electromagnetic valve V1, V2B, V3A, V4A, other magnetic valve V2A, V3B, V4B open.So refrigerant is in cooling and add in the temperature loops (series loop) and circulate, and according to the heat pump mode chamber B after cup A and the cooling that heats.
Namely, according to compressor 1 and the compressed high pressure-temperature gaseous coolant (hot gas) that forms gets around condenser 2, accumulator 3 and expansion valve 4A, from refrigerant pipeline L1, by bypass line L8, bypass line L9A and refrigerant pipeline L4A, and be imported into the evaporimeter 5A of cup A, and, gaseous coolant, when by bypass line L9A, according to flow regulator 14A, be limited flow and be depressurized, its adiabatic condensation temperature descends a little.
And, be imported into the gaseous coolant among the evaporimeter 5A of cup A, in the evaporimeter 5A of performance as the function of condenser, according to condensing and heat release, the cup A that heats, the major part of described gaseous coolant liquefies owing to condensing.So, the refrigerant after liquefying according to condensing in evaporimeter 5A by refrigerant pipeline L5A, refrigerant return pipe road L10A, and refrigerant return pipe road L11, and is imported into accumulator 3, so liquid refrigerants can be stored in accumulator 3.And from accumulator 3, the liquid refrigerants of high pressure can be imported into the evaporimeter 5B of rear chamber B by refrigerant pipeline L4B from refrigerant pipeline L3, and liquid refrigerants is by refrigerant pipeline L4A the time, and 4B is depressurized according to expansion valve.
As above-mentioned, the liquid refrigerants (part can become gaseous state) after being depressurized according to expansion valve 4B, in evaporimeter 5B, from around capture evaporation latent heat, so rear chamber B can be cooled.And, for the refrigerant that cools off rear chamber B according to evaporation, flow and arrival hydraulic accumulator 6 from refrigerant pipeline L5B toward refrigerant pipeline L6, by gas-liquid separation, then, only gaseous coolant flows through refrigerant pipeline L7 and is attracted in the compressor 1 in this hydraulic accumulator 6.Then, gaseous coolant is compressed once again according to compressor 1, repeatedly carries out later on same heat pump cycle, so cup A is heated and rear chamber B is cooled.
4) running stops:
Running stops, with good grounds be installed in respectively the not shown thermostat (thermostat) among cup A and the rear chamber B and make situation that temperature adjustment stops, and because the situation that the running end of refrigerating plant stops; In the former situation, as shown in figure 10, magnetic valve V1, magnetic valve V3A and V3B are opened (magnetic valve V1 is owing to be normally open valve, and energising just can not opened), and other magnetic valve V2A, V2B, V4A, V4B are closed; In the latter's situation, only magnetic valve V1 is opened, and all other magnetic valve V2A, V2B, V3A, V3B, V4A, V4B are closed.
5) defrosting running:
5-1) the defrosting of cup A running:
For the frosting that is attached on the evaporimeter 5A (being arranged among the cup A), when being melted the situation of removing, then carry out with above-mentioned heating-identical running shuts down, according to compressor 1 and the compressed HTHP gaseous coolant (hot gas) that forms, be imported among the evaporimeter 5A, according to the heat release of this gaseous coolant, the frosting meeting is removed.
The defrosting of chamber B running 5-2):
For the frosting that is attached on the evaporimeter 5B (being arranged among the rear chamber B), when being melted the situation of removing, then carry out and the above-mentioned stopping-identical running of running of heating, according to compressor 1 and the compressed HTHP gaseous coolant (hot gas) that forms, be imported among the evaporimeter 5B, according to the heat release of this gaseous coolant, the frosting meeting is removed.
More than, for the refrigerating plant of this example, the wherein cooling of one or both of cup A and rear chamber B, be with common refrigerating plant similarly, according to refrigerant is carried out wherein evaporating in one or both of evaporimeter 5A, 5B; Wherein the heating of one or both of cup A and rear chamber B, to make the high pressure-temperature gaseous coolant (hot gas) that spues from compressor 1, get around condenser 2, accumulator 3 and expansion valve 4A, 4B, import evaporimeter 5A, 5B wherein one or both, and according to make described refrigerant this evaporimeter 5A, 5B wherein in one or both heat release carry out (hot gas mode).
Again, as cooling cup A (or after chamber B) and the situation of rear chamber B (or the cup A) that heat, make the refrigerant that spues from compressor 1, get around condenser 2 and a side expansion valve 4B (or 4A) wherein, and flow among a side's wherein the evaporimeter 5B (or 5A), according to the liquefaction of the described refrigerant rear chamber B (or cup A) that heats, then refrigerant flows to expansion valve 4A (or 4B) and evaporimeter 5A (or 5B) after making liquefaction, according to the refrigerant evaporation that makes after the liquefaction, can cool off cup A (or rear chamber B).This kind mode is so-called heat pump mode, therein in rear chamber of the side (or cup A), evaporimeter 5B (or 5A) performance is as the function of condenser, gaseous coolant is condensed and make phase change, follow this phase change effect, can effectively utilize the large latent heat of condensation of heat and be used as thermal source, thereby can improve the efficient of heating of rear chamber B (or cup A).
And, refrigerant after the liquefaction, after being depressurized according to expansion valve 4A (or 4B), be imported among the opposing party's the evaporimeter 5A (or 5B) of cup A (or rear chamber B) and evaporate, thus can from around capture evaporation latent heat and energy efficiency is cooled off the opposing party's cup A (or afterwards chamber B) well.Like this, in the refrigerating plant of this example, owing to be to adopt heat pump mode, described heat pump mode is the latent heat that utilizes heat between cup A and rear chamber B to move and follow the required or generation of the phase change of refrigerant, cool off and heat, therefore, can effectively utilize heat energy to improve cooling and the ability of heating, and can shorten the start-up time of device.
Again, in cooling and when running of heating, do not use condenser 2, make refrigerant circulation owing to get around condenser 2, thus can side by side cool off running and heat running, and energy efficiency is cooled off goodly and is heated.
And then, in the refrigerating plant of this example, when cooling off and heating running, refrigerant condenses in the evaporimeter 5A (or 5B) of cup A (or rear chamber B) and liquefies, and the refrigerant after will liquefying stores in accumulator 3, then, the liquid refrigerants that sends from accumulator 3, after being depressurized according to expansion valve 4B (or 4A), flow among the evaporimeter 5B (or 5A) of rear chamber B (or cup A), and make its evaporation, and can be used for cooling off rear chamber B (or cup A), and the running of cooling off unchangeably and heat.Again, for example, in the situation that makes the refrigerant circulation quantity not sufficient in the refrigerant loop owing to the running of heating, open magnetic valve V5, refrigerant is replenished pipeline L12 through refrigerants and is supplemented to the low-pressure side loop of compressor 1 from accumulator 3, can supply refrigerant circulation whereby.
Again, in the refrigerating plant of this example, when heating running, from the refrigerant that compressor 1 spues, get around condenser 2 and expansion valve 4A, 4B, flow to evaporimeter 5A, 5B before, limit the flow of this refrigerant and refrigerant is reduced pressure according to flow regulator 14A, 14B, owing to make this kind formation, the adiabatic condensation temperature of this refrigerant descends, and condenses in evaporimeter 5A, 5B and can suppress to a certain extent refrigerant.
And then, refrigerating plant according to this example, design temperature for cup A and rear chamber B, mensuration temperature according to the cup A that measures according to temperature sensor 9,10 and rear chamber B, controller 17 couples of magnetic valve V1, V2A, V2B, V3A, V3B, V4A, V4B carry out open and close controlling, can selectively carry out whereby " cooling running ", " running of heating " reaches " cooling off and the running of heating ".
Again, the refrigerating plant of this example, when coming cup A and rear chamber B heated according to the running of heating, become setting value when following with specified period or when the suction pressure according to the detected compressor 1 that comes of pressure sensor 13, open magnetic valve V5, refrigerant is supplemented to the low-pressure side loop of compressor 1 from accumulator 3, owing to make this kind formation, even the winding number of refrigerator changes significantly, also can prevent the such unfavorable condition of refrigerant circulation quantity not sufficient in refrigerant loop.
Other, refrigerating plant according to this example, installing magnetic valve V1, described magnetic valve V1 with so that the refrigerant that spues from compressor 1 toward the flow disruption of condenser 2 directions or unimpeded, be positioned at the running of heating of closed condition as this magnetic valve V1, or the pressure that spues of compressor 1 becomes more than the setting value when cooling off and heat running, then open magnetic valve V1, make the refrigerant drainage of a part, if and the pressure that spues of compressor 1 becomes the tolerance bound definite value when above, stop the running of compressor 1, owing to make this kind formation, can prevent that the abnormal pressure in refrigerant loop from rising, guarantee high security.
Again, refrigerating plant according to this example, make condenser 2 and evaporimeter 5A, the refrigerant of the inside of 5B, no matter be the cooling running, the running of heating, any situation of cooling and the running of heating, when passing through the inside of these parts, refrigerant flows toward equidirectional always, owing to make this kind formation, when change temperature adjustment pattern, do not need to make compressor 1 to stop, and, can freely change the temperature adjustment pattern of cup A (or rear chamber B), can not be subject to the impact of the temperature adjustment pattern of rear chamber B (or cup A), for the operation of the dispensing of van cooler etc., described van cooler can repeatedly be advanced at short notice or stop and engine is stopped continually, can obtain a kind of effect that the revolution of engine can be effectively utilized in the running of refrigerating plant.
Also have, the form that applies the present invention in the refrigerating plant more than has been described, described refrigerating plant will be installed on the van cooler, and still, for other the arbitrarily refrigerating plant that will be installed in beyond the van cooler, the present invention also can similarly be applied certainly.
Claims (8)
1. refrigerating plant install respectively evaporimeter in two compartments, and described refrigerating plant comprises:
Cooling circuit, described cooling circuit, make that refrigerant sequentially flows through compressor, condenser at least, one of them side in one of them side in two expansion valves installing corresponding to each compartment and above-mentioned two evaporimeters that are connected in parallel, cool off one of them side in two compartments;
Add temperature loops, the described temperature loops that adds makes the refrigerant that spues from above-mentioned compressor, gets around above-mentioned condenser and above-mentioned expansion valve and flows to one of them side in two evaporimeters, one of them side in two compartments of heating whereby; And
Cooling and add temperature loops, described cooling and add temperature loops, make the refrigerant that spues from above-mentioned compressor, get around above-mentioned condenser and an above-mentioned wherein side expansion valve, flow in a side's wherein the evaporimeter and liquefy, then a wherein side the compartment of heating whereby makes refrigerant after the liquefaction flow to the opposing party's expansion valve and the opposing party's evaporimeter and makes its evaporation, cools off whereby the opposing party's compartment.
2. refrigerating plant as claimed in claim 1, wherein:
Between the above-mentioned condenser and above-mentioned expansion valve of above-mentioned cooling circuit, the installing accumulator, and be equiped with refrigerant return pipe road and the additional pipeline of refrigerant; Described refrigerant return pipe road makes by the refrigerant behind the above-mentioned evaporimeter to be back in the above-mentioned accumulator; Described refrigerant replenishes pipeline, from accumulator refrigerant is supplemented to the low-pressure side loop of above-mentioned compressor.
3. refrigerating plant as claimed in claim 1, wherein:
On bypass line, the installing flow is adjusted means; Described bypass line makes the refrigerant that spues from above-mentioned compressor, gets around above-mentioned condenser and above-mentioned expansion valve, and flows in each evaporimeter.
4. refrigerating plant as claimed in claim 1, wherein:
At most open and close valves of refrigerant pipeline installing, and described refrigerating plant is equiped with control device, in order to control the switching of each open and close valve; Described refrigerant pipeline is in order to consist of above-mentioned cooling circuit, above-mentionedly to add temperature loops, and above-mentioned cooling and add temperature loops.
5. refrigerating plant as claimed in claim 4, wherein:
Installing temperature detection means in above-mentioned each compartment, above-mentioned control device, design temperature for each compartment, mensuration temperature according to each compartment of measuring according to the said temperature detection means, come above-mentioned open and close valve is carried out open and close controlling, come whereby selectively to cool off running, the running of heating, and the cooling and the running of heating;
Described cooling running is that refrigerant is flowed in above-mentioned cooling circuit, cools off one of them side in two compartments;
The described running of heating is to make refrigerant flow one of them side in two compartments of heating in above-mentioned adding in the temperature loops;
Described cooling and the running of heating are to make refrigerant in above-mentioned cooling and add in the temperature loops to flow, and cool off a wherein side compartment, and the opposing party's that heats compartment.
6. refrigerating plant as claimed in claim 5, wherein:
Replenish pipeline at above-mentioned refrigerant and install open and close valve, and in the pressure detecting means of refrigerant pipeline installing in order to the suction pressure that detects above-mentioned compressor and the pressure that spues, above-mentioned control device, when coming two compartments are heated according to the above-mentioned running of heating, become setting value when following with specified period or when the suction pressure according to the detected compressor that comes of above-mentioned pressure detecting means, open above-mentioned open and close valve, refrigerant is supplemented to the low-pressure side loop of compressor from above-mentioned accumulator.
7. refrigerating plant as claimed in claim 6, wherein:
The installing open and close valve, described open and close valve with so that the refrigerant that spues from above-mentioned compressor toward the flow disruption of above-mentioned condenser direction or unimpeded, when above-mentioned open and close valve is positioned at the running or become more than the setting value according to the pressure that spues of the detected compressor that comes of above-mentioned pressure detecting means in cooling and when running of heating of heating of closed condition, then open above-mentioned open and close valve, if and the pressure that spues of compressor becomes the tolerance bound definite value when above, stop the running of compressor.
8. such as each the described refrigerating plant in the claim 5～7, wherein:
Flow through the refrigerant of above-mentioned condenser and above-mentioned evaporimeter, no matter be any situation of above-mentioned cooling running, the above-mentioned running of heating, above-mentioned cooling and the running of heating, all flow toward equidirectional.
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| CN201110291369.9A CN103017403B (en) | 2011-09-23 | 2011-09-23 | Refrigerating plant |
| HK13106185.7A HK1179332A1 (en) | 2011-09-23 | 2013-05-24 | Refrigerating installation |
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| CN201110291369.9A CN103017403B (en) | 2011-09-23 | 2011-09-23 | Refrigerating plant |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103363747A (en) * | 2013-07-04 | 2013-10-23 | 福建工程学院 | Direct-expansion type ground source heat pump start protection device and protection method thereof |
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| JPH07225063A (en) * | 1994-02-15 | 1995-08-22 | Daikin Ind Ltd | Cooling and heating apparatus with bathtub heating function |
| JPH09229507A (en) * | 1996-02-22 | 1997-09-05 | Toupure Kk | Air conditioner |
| JP2004162998A (en) * | 2002-11-13 | 2004-06-10 | Mitsubishi Heavy Ind Ltd | Refrigeration unit for vehicle and its control method |
| JP2005048981A (en) * | 2003-07-30 | 2005-02-24 | Mitsubishi Heavy Ind Ltd | Refrigeration unit |
| JP2005241045A (en) * | 2004-02-24 | 2005-09-08 | Sanyo Electric Co Ltd | Air conditioner |
| CN101983392A (en) * | 2008-09-24 | 2011-03-02 | 富士电机零售设备系统株式会社 | Vending machine |
-
2011
- 2011-09-23 CN CN201110291369.9A patent/CN103017403B/en active Active
-
2013
- 2013-05-24 HK HK13106185.7A patent/HK1179332A1/en not_active IP Right Cessation
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH07225063A (en) * | 1994-02-15 | 1995-08-22 | Daikin Ind Ltd | Cooling and heating apparatus with bathtub heating function |
| JPH09229507A (en) * | 1996-02-22 | 1997-09-05 | Toupure Kk | Air conditioner |
| JP2004162998A (en) * | 2002-11-13 | 2004-06-10 | Mitsubishi Heavy Ind Ltd | Refrigeration unit for vehicle and its control method |
| JP2005048981A (en) * | 2003-07-30 | 2005-02-24 | Mitsubishi Heavy Ind Ltd | Refrigeration unit |
| JP2005241045A (en) * | 2004-02-24 | 2005-09-08 | Sanyo Electric Co Ltd | Air conditioner |
| CN101983392A (en) * | 2008-09-24 | 2011-03-02 | 富士电机零售设备系统株式会社 | Vending machine |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103363747A (en) * | 2013-07-04 | 2013-10-23 | 福建工程学院 | Direct-expansion type ground source heat pump start protection device and protection method thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| HK1179332A1 (en) | 2013-09-27 |
| CN103017403B (en) | 2016-08-03 |
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